Inverter type scroll compressor

ABSTRACT

The present invention relates to an inverter type scroll compressor and comprises a housing, a fixed scroll which is set up inside the housing, an orbiting scroll which orbits around the fixed scroll, a driving unit which turns the orbiting scroll, an intake port and a discharge port which are in the housing, and an inverter which faces the front surface of the fixed scroll. An intake hole penetrating to the compression chamber and a discharge hole are respectively formed in the fixed scroll and the orbiting scroll. Accordingly, the present invention is configured so that the coolant is discharged through the discharge hole after the coolant passes through the inverter and the fixed scroll and then flows into the compression chamber.

TECHNICAL FIELD

The present invention relates to an inverter type scroll compressor, and more particularly to an inverter type scroll compressor which reduces power consumption and remarkably enhances efficiency by simultaneously cooling an inverter and compressed coolant using suctioned coolant.

BACKGROUND ART

In general, a scroll compressor includes a fixed scroll which has a spiral scroll wrap and maintains its fixed state regardless of rotation of a drive shaft, and an orbiting scroll which also has a spiral scroll wrap and orbits during rotation of the drive shaft. In such a scroll compressor, the orbiting scroll orbits with respect to the fixed scroll with coolant being suctioned into a compressor chamber formed between the fixed scroll and the orbiting scroll, so as to compress the coolant.

An example of such a scroll compressor is disclosed in FIG. 1 (hereinafter, referred to as ‘the conventional scroll compressor’) and will be schematically described with reference to FIG. 1.

As illustrated in the figure, an electromotive scroll compressor includes a housing 10, a suction port 60 and a discharge port 70 formed in the housing 10, a fixed scroll 81 and an orbiting scroll 82 accommodated within the housing 10 and engaged with each other, a drive shaft 83, a motor 84, a sliding bush 85 installed between a tip end of the drive shaft 83 and the orbiting scroll 82 to induce orbiting movement (revolution) of the orbiting scroll 82, and a rotation preventing unit 86 for preventing rotation of the orbiting scroll 82.

The suction port 60 and a suction chamber 13 are formed on the rear side of the housing 10 and the discharge port 70 and a discharge chamber 73 are formed on the front side of the housing 10.

An inverter 20 is sealingly installed on a side surface of the main housing 10.

The coolant which has passes through the suction chamber 13, a suction opening 16, and a space 17 below the inverter 20 is introduced into a compression chamber (a space between the fixed scroll and the orbiting scroll) 88 through a communication passage 15 and flows to a condenser via a discharge opening 811 formed in the fixed scroll 81, the discharge chamber 73, and the discharge port 70.

However, according to the conventional scroll compressor, since immediately after cooling the inverter 20, it is introduced into the compression chamber 88, the compressed coolant in the compression chamber 88 is heated.

Thus, the efficiency of the compressor lowers and its power consumption increases. That is, as the temperature increases during a compression operation, its isentropic efficiency lowers and its power consumption increases.

Furthermore, since the suctioned gas is adjacent to the discharge chamber 73, the efficiency of the compressor lowers due to heating.

Furthermore, according to the conventional scroll compressor, when the overheating degree of the compressor is lowered to increase the heat exchange efficiency of the evaporator (not shown), the suctioned coolant which has not deviated a liquid state region is compressed and wet-compressed, resulting in damage to the compressor.

DISCLOSURE Technical Problem

Therefore, it is an object of the present invention to provide an inverter type scroll compressor which prevents overheating of the compressor and remarkably increases the efficiency of the compressor by simultaneously cooling the inverter and the compression coolant using a suctioned coolant.

It is another object of the present invention to provide an inverter type scroll compressor which reduces power consumption by increasing the efficiency of the compressor.

It is still another object of the present invention to increase the heat exchange efficiency of an evaporator by lowering the overheating degree of the compressor when coolant is initially suctioned.

Technical Solution

In order to achieve the above-mentioned objects, there is provided an inverter type scroll compressor comprising: a housing; a fixed scroll fixed to and installed within the housing; an orbiting scroll configured to orbit with respect to the fixed scroll; a drive unit configured to drive and orbit the orbiting scroll; a suction port and a discharge port formed in the housing; and an inverter disposed on the front surface of the fixed scroll to be opposite to the fixed scroll, wherein a suction opening is formed in the fixed scroll to penetrate the fixed scroll to the compression chamber, a discharge opening is formed in the orbiting scroll, and coolant is discharged through the discharge opening after introduced into the compression chamber through the suction opening via a gap between the inverter and the fixed scroll.

A guide for guiding the coolant suctioned from the suction port to the suction opening may be formed on a front wall of the fixed scroll opposite to the inverter.

An introduction opening communicated with the suction opening of the fixed scroll may be formed in the guide.

When seen from the direction of the drive shaft, a plurality of guide channels may extend around the guide.

One end of at least one of the guide channels is disposed near the suction port and an opposite end thereof is disposed near the introduction opening.

At least one section of the guide channel may be arcuate.

At least one of the guide channels may have a linear introduction section on the side of the suction port.

The guide channels may be formed by a plurality of guide strips or guide grooves.

The discharge port may be formed on the rear side of the orbiting scroll.

A discharge passage may pass through the drive shaft along the lengthwise direction thereof.

At least one section of the discharge passage formed in the drive shaft may be inclined from the axis of the drive shaft to the outside as it goes from the rear side to the front side.

ADVANTAGEOUS EFFECT

According to the present invention, overheating of a compressor due to an inverter is prevented by simultaneously cooling the inverter and compression coolant using suctioned coolant, making it possible to remarkably increase the efficiency of the compressor.

Further, consumption of power for compression can be remarkably reduced due to increase in the efficiency of the compressor.

Furthermore, the heat exchange efficiency of an evaporator can be enhanced by lowering overheating degree when the coolant is initially suctioned.

In addition, a discharge chamber is prevented from being overheated by spacing suction gas far apart from the discharge chamber, making it possible to lower the efficiency of compression efficiency.

DESCRIPTION OF DRAWINGS

FIG. 1 is a longitudinal sectional view illustrating a conventional inverter type scroll compressor;

FIG. 2 is a longitudinal sectional view illustrating an inverter type scroll compressor according to the present invention;

FIG. 3 is a longitudinal sectional view illustrating a circulation structure for a suctioned coolant in the inverter type scroll compressor according to the present invention;

FIG. 4 is an exploded perspective view illustrating the inverter type scroll compressor according to the present invention;

FIG. 5 is a front perspective view in which an inverter is removed from FIG. 2;

FIG. 6 is a P-H graph of a suctioned coolant which passes through the inverter type scroll compressor according to the present invention; and

FIG. 7 is a P-H graph of a suctioned coolant which passes through the conventional inverter type scroll compressor.

MODE FOR INVENTION

Hereinafter, an exemplary embodiment of the present invention will be described in detail with reference to FIGS. 2 to 5.

As illustrated in the figures, the inverter type scroll compressor 1000 according to the present invention includes a housing 100, a suction port 600 and a discharge port 700 formed in the housing 100, a fixed scroll 810 and an orbiting scroll 820 accommodated within the housing 100 and engaged with each other, a drive shaft 830, a motor 840, a sliding bush 850 installed between a tip end of the drive shaft 830 and the orbiting scroll 820 to induce orbiting movement (revolution) of the orbiting scroll 820, and a rotation preventing unit 860, such as an Oldham ring, for prevent rotation of the orbiting scroll 820. The drive shaft 830, the drive motor 840, the sliding bush 850, and the rotation preventing unit 860 constitutes a orbiting movement driving unit of the orbiting scroll 820.

Referring to FIGS. 2 and 4, the housing 100 includes a front inverter housing 110, a rear main housing 130, and a main frame 120 disposed between the inverter housing 110 and the main housing 130. However, various well-known examples may be used for the housing 100.

The suction port 600 and the discharge port 700 are formed in the housing 100 such that coolant is suctioned through the suction port 600 from an evaporator, and after compressed in the compression chamber 880 between the fixed scroll 810 and the orbiting scroll 820, it is sent to a condenser through the discharge port 700.

In particular, according to the present invention, an inverter 200 is disposed on the front surface of the fixed scroll 810 to be opposite to the fixed scroll 810, and a suction opening 815 passes through the fixed scroll 810 to the compression chamber 880. The suction opening 815 is formed in the vicinity of the outer periphery of the fixed scroll 810 such that the suctioned coolant is discharged while it is compressed from the outer periphery of the fixed scroll 810 toward the center thereof.

A guide 900 for guiding the coolant suctioned from the suction port 600 to the suction opening 815 is formed on the front surface of the fixed scroll 810 opposite to the inverter 200.

Accordingly, the suctioned coolant flows between the inverter 200 and the guide 900 to simultaneously cool the inverter 200 and the compression chamber 880.

Meanwhile, the guide 900 may be omitted such that the suctioned coolant passes between the inverter 200 and the fixed scroll 810 and the coolant is suctioned into the compression chamber 880 through the suction opening 815 of the fixed scroll 810.

The coolant which has passed through the compression chamber 880 passes through the discharge opening 821 formed in the orbiting scroll 820 and then is discharged through the discharge port 700.

Although the suction coolant passes through the rear end of the housing 100 to be discharged, through a discharge passage 835 within the drive shaft 830 in the lengthwise direction of the drive shaft 830 in the figures, it is not compulsory to pass the discharge passage 835 through the drive shaft 830.

Meanwhile, as illustrated in the figures, an introduction opening 910 communicated with the suction opening 815 of the fixed scroll 810 may be formed in the guide 900. With this structure, the suctioned coolant flows into the compression chamber 880 after guided through the guide 900.

When seen from the direction of the drive shaft, a plurality of guide channels 920 extends around the guide 900. In this case, one end of at least one of the guide channels 920 is disposed near the suction port 600, and an opposite end thereof is disposed near the introduction opening 910.

Accordingly, the coolant uniformly cools the inverter 200 and the compression chamber 880 when the coolant is guided from the suction port 600 to the introduction opening 910.

In particular, when the suction port 600 is formed in a side wall of the housing 100, a portion of the guide channel 920 has a linear introduction section 921 on the side of the suction port 600 and the remaining portions of the guide channel 920 has a arcuate guide 922 to uniformly cool the compression chamber 880. That is, after the coolant is rapidly introduced through the linear introduction section 921 while it is being suctioned, it passes through the arcuate guide 922 to uniformly cool the front surface of the compression chamber 880. The suction coolant which has finished the cooling operation is introduced to the compression chamber 880 through the introduction opening 910 and the suction opening 815.

As illustrated in the figures, according to the present invention, since the discharge port 700 is located on the rear side of the orbiting scroll 820, the suctioned coolant is considerably spaced apart from the discharge side. Accordingly, the suction coolant is prevented from being influenced by the discharge side, making it possible to completely show its cooling effect.

As illustrated in the figures, although the guide channels 920 are formed by a plurality of guide strips 923, they may be formed by guide grooves.

Meanwhile, the discharge passage 835 formed in the drive shaft 830 is partially inclinedly formed from the axis of the drive shaft 830 to the outside as it goes from the rear side to the front side. With this structure, the coolant which comes to contain oil while it is passing through the compression chamber 880 is separated to gas and liquid oil by the centrifugal force. Then, the separated oil flows backward in the discharge passage 835 to be supplied to the main bearing 870.

Hereinafter, the circulating/cooling operations of the suctioned oil in the inverter type scroll compressor according to the present invention will be described with reference to FIGS. 2 and 3.

First, the suctioned coolant is introduced through the suction port 600 formed in the housing 100 from an evaporator (not shown).

Then, the coolant maintains a very low temperature and contains a small amount of liquid.

When the suctioned coolant passes the guide 900 between the inverter 200 and the fixed scroll 810, it simultaneously cools the inverter 200 and the compression chamber 880 and is heated to a suitable overheating degree at the same time.

The suctioned coolant which has completely passed through the guide 900 is introduced into the compression chamber 880 through the introduction opening 910 of the guide 900 and the suction opening 815 of the fixed scroll 810.

While the compression operation is being performed in the compression chamber 880, the following suctioned coolant performs a cooling operation. The cooling operation during the compression process reduces the power required for the compression to a predetermined pressure.

The coolant which has finished the compression process passes through the discharge opening 821 formed in the orbiting scroll 820 and is discharged through the discharge port 700.

In particular, in the figures, since the discharge passage 835 penetrates the drive shaft 830 along the lengthwise direction of the drive shaft 830, the coolant which has passed through the discharge opening 821 passes by the rear end of the housing 100 and is discharged to the discharge port 700 through a passage formed between the drive motor and the housing 100.

For this purpose, a radially extending groove 170 through which the coolant passes may be formed at the rear end of the housing 100.

The reference numerals 710 and 720 represents gaskets.

FIG. 6 illustrates a P-H (pressure-enthalpy) graph representing a cooling cycle of the inverter type scroll compressor according to the present invention. Hereinafter, a cooling cycle will be described with reference to the accompanying drawing.

In the graph, the sections A-B-C-D-E-F represent the process of circulating coolant. More particularly, the section A-D corresponds to a compressor, the section D-E to a condenser, the section E-F to an expansion valve, and the section F-A to an evaporator.

As illustrated in the figure, according to the present invention, the suctioned coolant at an introduction section A of the compressor contains liquid. That is, as the volume occupied by liquid within the evaporator becomes larger, the heat exchange efficiency increases.

In the graph, the section A→B represents a state in which the temperature of the coolant increases while the inverter 200 is being cooled and the section B→C represents a state in which the temperature of the coolant increases while the coolant compressed within the compression chamber 880 is cooled. In this way, the two cooling procedures makes the suctioned coolant completely gaseous and maintains the suctioned coolant at a suitable overheating degree.

Next, the section C→D represents a process of compressing the actually suctioned coolant. However, since the coolant which is being compressed during the compression process is cooled by the suctioned coolant, it reaches a predetermined pressure at a rapid inclination. That is, the compression process is finished with little power consumption.

In the graph, the dotted line represents an isentropic process and shows a theoretical relation.

As illustrated in the figure, according to the present invention, the isentropic efficiency defined by the power of the isentropic process (PAs) with respect to the power (work) of the actual process (PAr) exceeds 100 percent.

For reference, FIG. 7 illustrates a cooling cycle of a conventional compressor in which the suction coolant cools only an inverter.

As illustrated in the figure, immediately after the coolant is heated while cooling the inverter through the section A′→B′, it enters a compression chamber, remarkably increasing the power consumed to obtain a predetermined pressure. That is, since the coolant compressed by the suctioned coolant in the compression chamber has no cooling effect, the efficiency of the compressor severely lowers as compared with the present invention.

In the graph, the dotted line represents an isentropic process and the isentropic efficiency cannot exceed 100 percent.

INDUSTRIAL APPLICABILITY

According to the present invention, overheating of a compressor due to an inverter is prevented by simultaneously cooling the inverter and compression coolant using suctioned coolant, making it possible to remarkably increase the efficiency of the compressor.

Further, consumption of power for compression can be remarkably reduced due to increase in the efficiency of the compressor.

Furthermore, the heat exchange efficiency of an evaporator can be enhanced by lowering overheating degree when the coolant is initially suctioned.

In addition, a discharge chamber is prevented from being overheated by spacing suction gas far apart from the discharge chamber, making it possible to lower the efficiency of compression efficiency. 

1. An inverter type scroll compressor comprising: a housing; a fixed scroll fixed to and installed within the housing; an orbiting scroll configured to orbit with respect to the fixed scroll; a drive unit configured to drive and orbit the orbiting scroll; a suction port and a discharge port formed in the housing; and an inverter disposed on the front surface of the fixed scroll to be opposite to the fixed scroll, wherein a suction opening is formed in the fixed scroll to penetrate the fixed scroll to the compression chamber, a discharge opening is formed in the orbiting scroll, and coolant is discharged through the discharge opening after introduced into the compression chamber through the suction opening via a gap between the inverter and the fixed scroll.
 2. The inverter type scroll compressor as claimed in claim 1, wherein a guide for guiding the coolant suctioned from the suction port to the suction opening is formed on a front wall of the fixed scroll opposite to the inverter.
 3. The inverter type scroll compressor as claimed in claim 2, wherein an introduction opening communicated with the suction opening of the fixed scroll is formed in the guide.
 4. The inverter type scroll compressor as claimed in claim 3, wherein, when seen from the direction of the drive shaft, a plurality of guide channels extends around the guide.
 5. The inverter type scroll compressor as claimed in claim 4, wherein one end of at least one of the guide channels is disposed near the suction port and an opposite end thereof is disposed near the introduction opening.
 6. The inverter type scroll compressor as claimed in claim 5, wherein at least one section of the guide channel is arcuate.
 7. The inverter type scroll compressor as claimed in claim 5, wherein at least one of the guide channels has a linear introduction section on the side of the suction port.
 8. The inverter type scroll compressor as claimed in claim 4, wherein the guide channels are formed by a plurality of guide strips or guide grooves.
 9. The inverter type scroll compressor as claimed in claim 1, wherein the discharge port is formed on the rear side of the orbiting scroll.
 10. The inverter type scroll compressor as claimed in claim 1, wherein the drive unit includes a drive shaft and a discharge passage passes through the drive shaft along the lengthwise direction thereof.
 11. The inverter type scroll compressor as claimed in claim 10, wherein at least one section of the discharge passage formed in the drive shaft is inclined from the axis of the drive shaft to the outside as it goes from the rear side to the front side. 